Turbine pumps

ABSTRACT

Embodiments of pumps are disclosed along with systems and methods relating thereto. In an embodiment, the pump includes a casing assembly that includes a central axis, an upstream connector that is configured to engage with a first connector on a fluid line, and a downstream connector that is configured to engage with a second connector on the fluid line. In addition, the pump includes an impeller rotatably disposed within the casing assembly. Further, the pump includes a driver assembly coupled to the casing assembly and annularly disposed about the impeller. The driver assembly is configured to rotate the impeller about the central axis.

CROSS-REFERENCE TO RELATED APPLICATIONS

Not applicable.

STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT

Not applicable.

BACKGROUND

Fluid pumps may include an impeller that is rotated to pressurize afluid (e.g., a liquid), Typically the impeller is driven by a motor orother suitable driver. In some circumstances, a pump may be used topressurize fluid that is corrosive, particularly to metallic materials.In such a service, metallic components of the pump that come intocontact with the fluid may experience corrosion, thereby decreasing thelifespan thereof.

SUMMARY

Some embodiments disclosed herein are directed to a pump. in anembodiment, the pump includes a casing assembly that includes a centralaxis, an upstream connector that is configured to engage with a firstconnector on a fluid line, and a downstream connector that is configuredto engage with a second connector on the fluid line. In addition, thepump includes an impeller rotatably disposed within the casing assembly.Further, the pump includes a driver assembly coupled to the casingassembly and annularly disposed about the impeller. The driver assemblyis configured to rotate the impeller about the central axis.

Other embodiments disclosed herein are directed to a system. In anembodiment, the system includes a first pipe section, a second pipesection, and a pump mounted between the first pipe section and thesecond pipe section. The pump includes a casing assembly including acentral axis. In addition, the pump includes an impeller rotatablydisposed within the casing assembly. Further, the pump includes a driverassembly coupled to the casing assembly and annularly disposed about theimpeller. The driver assembly is configured to rotate the impeller aboutthe central axis to pump fluid from the first pipe section to the secondpipe section.

Still other embodiments disclosed herein are directed to a method ofpumping a fluid through a fluid line. in an embodiment, the methodincludes (a) mounting a pump between a pair of pipe sections of thefluid line. The pump includes a casing assembly including a centralaxis, an impeller rotatably disposed within the casing assembly, and adriver assembly coupled to the casing assembly and annularly disposedabout the impeller. In addition, the method includes (b) rotating theimpeller about the central axis with the driver assembly. Further, themethod includes (c) flowing a fluid through the pair of pipe sectionsand the pump during (b).

Embodiments described herein comprise a combination of features andcharacteristics intended to address various shortcomings associated withcertain prior devices, systems, and methods. The foregoing has outlinedrather broadly the features and technical characteristics of thedisclosed embodiments in order that the detailed description thatfollows may be better understood. The various characteristics andfeatures described above, as well as others, will be readily apparent tothose skilled in the art upon reading the following detaileddescription, and by referring to the accompanying drawings. It should beappreciated that the conception and the specific embodiments disclosedmay be readily utilized as a basis for modifying or designing otherstructures for carrying out the same purposes as the disclosedembodiments. It should also be realized that such equivalentconstructions do not depart from the spirit and scope of the principlesdisclosed herein.

BRIEF DESCRIPTION OF THE DRAWINGS

For a detailed description of various exemplary embodiments, referencewill now be made to the accompanying drawings in which:

FIG. 1 is a side view of a pump system according to some embodiments;

FIG. 2 is a side cross-sectional view of a pump for use in the pumpsystem of FIG. 1 according to some embodiments;

FIGS. 3 and 4 are side cross-sectional views of a suction casing and adischarge casing, respectively, of the pump of FIG. 2;

FIG. 5 is a side cross-sectional view of an impeller of the pump of FIG.2;

FIG. 6 is a side cross-sectional view of a thermal transfer assembly ofthe pump of HG.

FIG. 7 is a side cross-sectional view of a. diffuser of the pump of FIG.2;

FIG. 8 is an exploded assembly view of the pump of FIG. 2;

FIGS. 9 and 10 are exploded assembly views of portions of the pump ofFIG. 2;

FIG. 11 is a cross-sectional view of the pump system of FIG. 1;

FIGS. 12 and 13 are schematic side views of embodiments of a thermaltransfer system for use with the pump of FIG. 2 according to someembodiments;

FIG. 14 is side cross-sectional view of a wax mold core formanufacturing an impeller of the pump of FIG. 2 according to someembodiments; and

FIGS. 15 and 16 are sequential perspective views of a molding processutilizing the wax mold core of FIG. 14 according to some embodiments.

DETAILED DESCRIPTION

The following discussion is directed to various exemplary embodiments.However, one of ordinary skill in the art will understand that theexamples disclosed herein have broad application, and that thediscussion of any embodiment is meant only to be exemplary of thatembodiment, and not intended to suggest that the scope of thedisclosure, including the claims, is limited to that embodiment.

The drawing figures are not necessarily to scale. Certain features andcomponents herein may be shown exaggerated in scale or in somewhatschematic form and some details of conventional elements may not beshown in interest of clarity and conciseness.

In the following discussion and in the claims, the terms “including” and“comprising” are used in an open-ended fashion, and thus should beinterpreted to mean “including, but not limited to . . .” Also, the term“couple” or “couples” is intended to mean either an indirect or directconnection. Thus, if a first device couples to a second device, thatconnection may be through a direct connection of the two devices, orthrough an indirect connection that is established via other devices,components, nodes, and connections. In addition, as used herein, theterms “axial” and “axially” generally mean along or parallel to a givenaxis (e.g., central axis of a body or a port), while the terms “radial”and “radially” generally mean perpendicular to the given axis. Forinstance, an axial distance refers to a distance measured along orparallel to the axis, and a radial distance means a distance measuredperpendicular to the axis. Further, when used herein (including in theclaims), the words “about,” “generally,” “substantially,”“approximately,” and the like mean within a range of plus or minus 10%.

As previously described, pumps may include an impeller that is driven orrotated by a separate driver or motor. Typically, the motor and/or thepump is supported on separate base or foundation (e.g., a concrete pad).Therefore, the location of pumps within a facility is typicallydetermined by the available floor spacing for the motor foundation. As aresult, additional lengths or runs of piping (or other conduit) may becalled for to fluidly couple the fluid lines to the potentially distallydisposed pump. Accordingly, embodiments disclosed herein include pumps(e.g., turbine pumps) including an integrated motor or driver that areconfigured to be coupled within and along a fluid line or pipe. Thus,through use of the embodiments disclosed herein, a foundation or basefor the pump (or the associated motor) is no longer included, and thearrangement of the pumps within a facility is greatly simplified.

Referring to FIG. 1, an embodiment of a pump system 1000 is shown.Generally speaking, system 1000 includes turbine pump 800 (or moregenerally “pump 800”) that is disposed along a fluid line 920. Inparticular, pump 800 is coupled between and in-line with a pair of pipeor conduit sections 920 a, 920 b such that a central or longitudinalaxis 805 (“axis 805”) of pump 800 is aligned with a central axis 925 offluid line 920. In this embodiment and as will be described in moredetail below, pump 800 is configured to induce or drive a flow of fluidalong fluid line 920 in a flow direction 950 from pipe section 920 a topipe section 920 b. Thus, pipe section 920 a may be referred to hereinas an “upstream pipe section,” and pipe section 920 b may be referred toherein as a “downstream pipe section.”

Referring now to FIGS. 2, generally speaking, turbine pump 800 comprisesa casing assembly 100, an impeller assembly 200, a driver assembly 300,a diffuser 500, and a thermal transfer assembly 400 all concentricallydisposed along axis 805. Driver assembly 300 and thermal transferassembly 400 are mounted to casing assembly 100 and impeller assembly200 and diffuser 500 are disposed within casing assembly 100. Ingeneral, during operations impeller assembly 200 is rotated about axis805 by driver assembly 300 to pressurize a fluid (e.g., a liquid) withinfluid line 920 (see e.g., FIG. 1) so that the fluid is flowed fromupstream pipe section 920 a toward and through downstream pipe section920 b along flow direction 950 as previously described. As will bedescribed in more detail below, some or all of the components of pump800 may be constructed from non-metallic materials so as to decrease theoverall weight of pump 800 and to avoid corrosion due to contact withpotentially corrosive fluids flowing therethrough (e.g., salt water).

Referring now to FIGS. 2-4 and 8, casing assembly 100 includes a firstor suction casing 102 and a second or discharge casing 120. Referringspecifically to FIGS. 3 and 9, suction casing 102 includes a first orupstream end 102 a, a second or downstream end 102 b opposite upstreamend 102 a, and a throughbore 104 extending axially between ends 102 a,102 b. In addition, suction casing 102 includes a first or upstreamconnector 106 at upstream end 102 a, a second or downstream connector108 proximate to downstream end 102 b, a cylindrical body 103 extendingaxially between connectors 106, 108, and a cylindrical projection or lip107 extending axially from downstream connector 108 to downstream end102 b. A seal gland 114 extends radially inward into lip 107 thatreceives a sealing member (e.g., O-ring) 150 therein.

Connectors 106, 108 may be any suitable device or structure for couplingwith a corresponding connector or device on fluid line 920 or withinpump 800 (see e.g., FIG. 1), such as, for example, flanges, couplings,threaded connectors, etc. In this embodiment, connectors 106, 108comprise flanges. Upstream connector 106 includes a planar engagementface or surface 106 a, and downstream connector 108 includes a planarengagement face or surface 108 a. Engagement surface 108 a of downstreamconnector 108 includes an axially extending circumferential groove orchannel 112. In addition, a plurality of bolt holes 116 and bolt holes118 may be provided through upstream connector 106 and downstreamconnector 108, respectively. Note that only one of the bolt holes 116and one of the bolt holes 118 are visible in FIGS. 2 and 3 due to thearrangement of the cross-sectional views shown therein.

A radially extending downstream facing annular shoulder 109 (“shoulder109”) is disposed within throughbore 104 such that throughbore 104includes a first or upstream section 104 a extending axially fromupstream end 102 a to shoulder 109 and second or downstream section 104b extending axially form shoulder 109 to downstream end 102 b.Downstream section 104 b has a larger inner diameter than upstreamsection 104 a.

Referring specifically to FIGS. 4 and 10, discharge casing 120 includesa first or upstream end 120 a, a second or downstream end 120 b oppositeupstream end 120 a, and a throughbore 124 extending axially between ends120 a, 120 b. In addition, discharge casing 120 includes a first orupstream connector 128 proximate to upstream end 120 a, a second ordownstream connector 126 at downstream end 120 b, a cylindrical body 123extending axially between connectors 128, 126, and a cylindricalprojection or lip 127 extending axially from upstream connector 128 toupstream end 120 a. A seal gland 134 extends radially inward intocylindrical projection 127 that receives a sealing member (e.g., O-ring)152 therein.

Connectors 126, 128 may similar to connectors 106, 108, previouslydescribed for suction casing 102 (see e.g., FIGS. 2 and 3). Thus,connector 126, 128 may be any suitable device or structure for couplingwith a corresponding connector or device on fluid line 920 or withinpump 800. In this embodiment, connectors 126, 128 comprise flanges.Downstream connector 126 includes a planar engagement face or surface126 a, and upstream connector 128 includes a planar engagement face orsurface 128 a. Engagement surface 128 a of upstream connector 128includes an axially extending circumferential groove or channel 132. Inaddition, a plurality of bolt holes 140 and bolt holes 142 may beprovided through upstream connector 128 and downstream connector 126,respectively, Note that only one of the bolt holes 140 and one of thebolt holes 142 are visible in FIGS. 2 and 4 due to the arrangement ofthe cross-sectional views shown therein.

A radially extending annular projection 136 (“projection 136”) isdisposed within throughbore 124 so that throughbore 124 includes a firstor upstream section 124 a extending axially from upstream end 120 a toprojection 136 and second or downstream section 124 b extending axiallyfrom projection 136 to downstream end 120 b. Projection 136 defines afirst or upstream facing annular shoulder 137 and a second or downstreamfacing annular shoulder 139. Upstream section 124 a has a larger innerdiameter than downstream section 124 b. Also, a radially extendingannular recess 138 is disposed within downstream section 124 b ofthroughbore 124.

Referring now to FIGS. 2, 5, 8, and 9, impeller assembly 200 generallyincludes an impeller 202, a pair of impeller wear rings 220 a, 220 b anda magnet assembly 230. Referring specifically to FIG-S. 5 and 9,impeller 202 comprises an outer housing 204, a central hub 206 disposedwithin outer housing 204, and a plurality of impeller vanes 208 (or moresimply “vanes 208”) extending between central hub 206 and outer housing204.

In this embodiment, outer housing 204 is a cylindrical member thatincludes a first or upstream end 204 a, a second or downstream end 204 bopposite upstream end 204 a. In addition, outer housing 204 includes aradially outer cylindrical surface 201 and a radially inner cylindricalsurface 203 both extending axially between ends 204 a, 204 b. In otherembodiments, outer housing 204 (or a portion thereof), may benon-cylindrical in shape,

Referring specifically to FIGS. 5 and 9, central hub 206 is a solidmember (non-hollow) that is disposed within outer housing 204 along axis805 and includes a first or upstream end 206 a, a second or downstreamend 206 b opposite upstream end 206 a. Upstream end 206 a is proximateupstream end 204 a of outer housing 204, and downstream end 206 b isdisposed at downstream end 204 b of outer housing 204. In thisembodiment, central hub 206 is generally^(,) conical in shape and thusincludes a varying cross-section between ends 206 a, 206 b. Inparticular, the circumference and diameter of central hub 206progressively increase between ends 206 a and 206 b. In addition, inthis embodiment upstream end 206 a includes a rounded or hemisphericalsurface 207. Without being limited to this or any other theory, thehemispherical surface 207 may reduce turbulence for the fluid flowingwithin outer housing 204 and the generally conical shape of central hub206 may progressively decrease the flow area within outer housing 204for fluids flowing from upstream end 204 a toward downstream end 204 b.This decrease in the flow area may increase the localized flow ratealong axis 805 and the pressure of the fluid flowing through impeller202 during operations. It should be appreciated that other shapes andprofiles are contemplated for central hub 206. For example, in someembodiments, central hub 206 may include non-linear cross-sectionchanges (e.g., a parabolic).

Vanes 208 extend generally radially from central hub 206 to radiallyinner cylindrical surface 203 of outer housing 204. In some embodiments,vanes 208 are circumferentially spaced (e.g., uniformlycircumferentially spaced) about axis 805. In addition, all or some ofthe vanes 208 may be axially spaced from one another along axis 805. Inthis embodiment, there are total three vanes 208, that arecircumferentially spaced approximately 120° from one another about axis805; however, other numbers and spacing are contemplated for vanes 208in other embodiments. In addition, each of the vanes 208 of thisembodiment extend generally helically (e.g., along a constant or varyinghelical pitch) about central hub 206 between ends 206 a, 206 b..

As best shown in FIG. 5, in this embodiment, each of the vanes 208 isgenerally curved between central hub 206 and radially inner cylindricalsurface 203 of outer housing 204. In particular, each vane 208 generallycurves in an upstream direction, or toward upstream ends 206 a, 204 a ofcentral hub 206 and outer housing 204 when moving radially outward fromcentral hub 206 toward radially inner cylindrical surface 203. However,it should be appreciated that vanes 208 may extend generally linearlybetween central hub 206 and radially inner cylindrical surface 203 inother embodiments. In addition, in this embodiment the axial thicknessof each vane 208 generally decreases when moving from central hub 206toward radially inner cylindrical surface 203. However, again, in otherembodiments, the axial thickness of vanes 208 may be generally constantbetween central hub 206 and radially inner cylindrical surface 203.Further, while not specifically shown it should be appreciated that theaxial thickness of each vane 208 may vary (e.g., increase and/ordecrease) or may remain generally constant between its correspondingupstream and downstream ends. Still further, in some embodiments localcross-sectional variations may be included along vanes 208 to optimizeflow characteristics through impeller 202 during operations.

In some embodiments the generally helical configuration of vanes 208 mayvary along the axial direction (e.g., along axis 805, between ends 206a, 206 b) and/or along the radial direction (e.g., radially betweencentral hub 206 and radially inner cylindrical surface 203 of outerhousing 204). For instance, in some embodiments vanes 208 may have avarying helical pitch along the axial length between ends 206 a, 206 b.Generally speaking, as the helical pitch increases the vanes 208 axiallyadvance a greater distance along axis 805 for a given amount of angulartwist about axis 805. Thus, in some embodiments the helical pitch ofvanes 208 at the first end 206 a is different from the helical pitch ofvanes 208 at second end 206 b. Additionally or alternatively, in someembodiments vanes 208 may have helical pitch which varies as a functionof radial position between central hub 206 and radially innercylindrical surface 203. For example, the helical pitch of vanes 208 mayincrease and/or decrease when moving radially from the attachmentcentral hub 206 and the radially inner cylindrical surface 203. However,it should be appreciated that other variations of the helical pitch ofvanes 208 (as well as other parameters) are contemplated herein.

Referring still to FIGS. 5 and 9, in this embodiment, outer housing 204,central hub 206 and vanes 208 are all formed as a monolithic piece ormember (i.e., impeller 202). Thus, in some embodiments, outer housing204, central hub 206, and vanes 208 may comprise the same material(s)(e.g., fiberglass). During operations, the impeller 202 (including outerhousing 204, central hub 206, and vanes 208) generally rotates aboutaxis 805 to increase the pressure and velocity of the fluid flowingtherethrough. In this embodiment, impeller 202 is symmetrical about axis805 such that its rotating moment of inertia is concentric about axis805. In addition because vanes 208 are monolithically formed with outerhousing 204 and central hub 206 as previously described, fluids flowingthrough impeller 202 (e.g., between ends 204 a, 204 b of outer housing204 are prevented from flowing between outer housing 204 and vanes 208and between vanes 208 and central hub 206. Accordingly, the fluid isforced to flow in a generally helical or twisting path about axis 805between vanes 208 as it flows axially between ends 204 a, 204 b of outerhousing 204.

Referring still to FIGS. 5 and 9, each impeller wear ring 220 a, 220 bincludes an annular base 222 including a central aperture 221 extendingaxially therethrough, and a cylindrical sleeve 223 extending axiallyfrom annular base 222. Each of the impeller wear rings 220 a, 220 b aredisposed on outer housing 204 of impeller 202, such that wear ring 220 ais disposed over upstream end 204 a of outer housing 204, and wear ring220 b is disposed over downstream end 204 b of outer housing 204. Inparticular, upstream end 204 a of outer housing 204 is received withinwear ring 220 a such that radially outer cylindrical surface 201 isengaged with the corresponding cylindrical sleeve 223 and upstream end204 a is engaged with the corresponding annular base 222. Similarly,downstream end 204 b of outer housing 204 is received within wear ring220 b such that radially outer cylindrical surface 201 is engaged withthe corresponding cylindrical sleeve 223 and downstream end 204 b isengaged with the corresponding annular base 222. In addition, oncemounted to outer housing 204 as described above, central apertures 221in wear rings 220 a, 220 b are aligned with radially inner surface 203.Thus, in this embodiment central apertures 221 are flush with radiallyinner cylindrical surface 203.

Referring still to FIGS. 5 and 9, magnet assembly 230 comprises acylindrical ring or sleeve 232, and a plurality of magnets 240 mountedto sleeve 232. In particular, sleeve 232. includes an axially extendingradially inner cylindrical surface 231 and an axially extending radiallyouter cylindrical surface 233. The plurality of magnets 240 are mountedto radially outer cylindrical surface 233. In particular, magnets 240are uniformly circumferentially spaced along radially outer cylindricalsurface 233 relative to axis 805. In this embodiment, magnets 240 arepermanent magnets; however, it should be appreciated that in otherembodiments magnets 240 may comprise electrically conductive materials(e.g., aluminum bars) such as may found within an induction rotor, ormay comprise one or more electro-magnetic coils (e.g., conductive coilsor windings, such as cooper, surrounding a ferromagnetic orferromagnetic core, such as iron).

As best shown in FIG. 5, magnet assembly 230 is disposed about outerhousing 204 of impeller 202 such that radially inner surface 231 ofsleeve 232 is engaged with radially outer cylindrical surface 201 ofouter housing 204. in addition, in this embodiment, sleeve 232 ispositioned axially between wear rings 220 a, 220 b such that sleeve 232is axially spaced from cylindrical sleeves 223 of each ring 220 a, 201),Further, in this embodiment, sleeve 232 is generally axially centeredbetween ends 204 a, 204 b of outer housing 204. Sleeve 232 may besecured to radially outer cylindrical surface 201 of outer housing 204in any suitable fashion. For example, in some embodiments, sleeve 232may be secured to outer housing 204 via a friction fit. In addition, inother embodiments, sleeve 232 may be welded, brazed, adhered (e.g., withan adhesive) or otherwise secured to outer housing 204.

Referring again to FIG. 2, during operations, impeller assembly 200 isdisposed axially between suction casing 102 and discharge casing 120. Inparticular, a pair of casing wear rings 210 a, 210 b are disposed withinthroughbores 104, 124 of casings 102, 120, respectively. Each casingwear ring 210 a, 210 b includes an annular base 212 including a centralaperture 211 extending axially therethrough, and a cylindrical sleeve213 extending axially from base 212 Casing wear ring 210 a is receivedwithin downstream section 104 b of throughbore 104 of suction casing 102such that the corresponding annular base 212 is engaged with annularshoulder 109 and the corresponding central aperture 211 is generallyaligned and flush with upstream section 104 a of throughbore 104.Similarly, casing wear ring 210 b is received within downstream section124 b of throughbore 124 of discharge casing 120 such that thecorresponding base 212 is engaged with upstream facing annular shoulder137.

As shown in FIG. 2, impeller assembly 200 is received within casingassembly 100 such that impeller wear ring 220 a is received withincasing wear ring 210 a and impeller wear ring 220 b is received withincasing wear ring 210 b. In particular, cylindrical sleeves 223 of wearrings 220 a, 220 b may slidingly engage with cylindrical sleeves 213 ofcasing wear rings 210 a, 210 b, respectively, and central apertures 221and 211 of wear rings 220 a, 220 b, and 210 a, 210 b, are generallyflush with one another along axis 805. As will be described in moredetail below, during operations, impeller assembly 200 rotates aboutaxis 805 within casing assembly 100 such that wear rings 220 a, 220 brotate within and relative to casing wear rings 210 a, 210 b,respectively. Accordingly, direct contact between outer housing 204 ofimpeller and casings 102, 120 is avoided, and wear rings 210 a, 210 b,220 a, 220 b may be considered wear parts that are replaced at regularintervals.

Referring still to FIGS. 2 and 10, driver assembly 300 is annularlydisposed about magnet assembly 230 and is axially positioned betweensuction casing 102 and discharge casing 120. In particular, as shown inFIG, 2 driver assembly 300 is disposed over the cylindrical projections107, 127, and is axially disposed between planar engagements faces 108a, 128 a of connectors 108, 128 of casings 102, 120, respectively. Inaddition, a sealing sleeve 330 is disposed radially between cylindricalprojections 107, 127 of casings 102, 120 and driver assembly 300, suchthat sealing members 150, 152 are radially compressed within seal glands114, 134 of casings 102, 120 (see e.g., FIGS. 3 and 4). Thus, fluids areprevented (or at least restricted) from flowing between seal sleeve 330and cylindrical projections 107, 127 during operations.

In this embodiment driver assembly 300 defines a plurality of windingsor coils 304 of conductive wire (e.g., conductive coils or windings,such as cooper, surrounding a ferromagnetic or ferromagnetic core, suchas iron) that are disposed or arranged circumferentially about axis 805.Generally speaking, during operations, electrical current may be routedthrough the conductive coils 304 so as to induce varying magneticfields. As will be described in more detail below, the induced magneticfields within driver assembly are configured to drive rotation ofimpeller assembly 200 about axis 805 within casing assembly 100 duringoperations.

It should be appreciated that driver assembly 300 may includealternative designs in other embodiments. For instance, in someembodiments, windings 304 may be replaced with a plurality of permanentmagnets arranged circumferentially around axis 805, or a plurality ofelectrically conductive members (e.g., aluminum bars) such as might beused within an induction motor.

Referring now to FIGS. 2, 6, and 9, thermal transfer assembly 400includes heat sink or body 402 and a cooling coil 420 circumferentiallywrapped around body 402. Body 402 includes a first or upstream end 402a, a second or downstream end 402 b opposite upstream end 402 a, and athroughbore 401 extending axially between ends 402 a, 402 b that isdefined by a radially inner cylindrical surface 407. In addition, body402 includes a first or upstream connector 404 proximate upstream end402 a, a second or downstream connector 406 proximate downstream end 402b, and a radially outer cylindrical surface 403 extending axiallybetween connectors 404, 406. Connectors 406, 408 may comprise anysuitable structure or device for mating with another component ormember. For instance, in this embodiment connectors 404, 406 comprisesflanges that each include a plurality of mounting bores 410 extendingaxially therein (note: only one of the mounting bores 410 are visible ineach of the connectors 404, 406 in FIGS. 2 and 6 due to the arrangementof the cross-sectional views shown therein) Further, in this embodimentbody 402 includes a first or upstream lip 409 a extending axiallyupstream connector 404 to upstream end 402 a, and a downstream secondlip 409 b extending axially from downstream connector 406 to downstreamend 402 b. Lips 409 a, 409 b may also be generally referred to herein as“axial projections 409 a, 409 b.”

Cooling coil 420 comprises an elongate tube or conduit that is wrapped(e.g., helically) about radially outer surface 403 of body 402. Coolingcoil 420 may comprise any suitable material, and in some embodiments maycomprise a conductive material (e.g., a metal) so as to conduct thermalenergy away from body 402 during operations. As will be described inmore detail below, during operations a cooling fluid (e.g., divertedfluid from fluid line 920, a separate cooling fluid, etc.) is flowed orrouted through cooling coil 420 to facilitate convective heat transfer,In this embodiment, cooling coil 420 comprises includes a circularcross-section; however, other cross-sections are contemplated (e.g.,elliptical, rectangular, square, etc.).

Body 402 may be constructed from any suitable material, and in sonicembodiments may be made of a material having a high thermal conductivity(e.g., having a coefficient of thermal conductivity above 5-W/m° K). Inaddition, in sonic embodiments, body 402 may be made from a non-magneticor possibly a weakly magnetic material (e.g., aluminum, 316 stainless,nickel alloys, alumina filled epoxy, etc.). In some embodiments, theremay be intimate contact between cooling coil 420 and radially outercylindrical surface 403 of body 402 since increased contact areas andcompressive forces may increase the heat flow capacity between body 402and cooling coil 420 during operations. In some embodiments, ridges,fins or other suitable projections may be disposed along body 402(particularly along radially outer surface 403) to increase thecircumferential contact area between each segment of cooling coil 420and body 402. In addition, in some embodiments, increased contact may beachieved between cooling coil 420 and body 402 by tightly wrappingcooling coil 420 around body 402 and/or by applying an external clamp(not shown) around the perimeter of cooling coil 420.

Referring again to FIG. 2, thermal transfer assembly 400 is engagedaxially between connectors 108, 128 of casings 102, 120, respectively.In particular, upstream connector 404 on body 402 is engaged with planarengagement surface 108 a on downstream connector 108 of upstream casingand downstream connector 406 on body 402 is engaged with engagementsurface 128 a on upstream connector 128 of discharge casing 120. Inaddition, upstream lip 409 a is received within circumferential groove112 in planar engagement face 108 a, and downstream lip 409 b isreceived within circumferential groove 132 in planar engagement face 128a. Further, a plurality of fasteners 160 (e.g., bolts) are receivedwithin aligned pairs of the bolt holes 118 on connector 108 of suctioncasing 102 and the mounting bores 410 on upstream connector 404 andwithin aligned pairs of the bolt holes 140 on upstream connector 128 andthe mounting bores 410 on downstream connector 406. In this embodiment,the fasteners extend through bolt holes 118, 140 and are threadablyengaged with the corresponding mounting holes 410 so as to secure body402 axially between each of the casings 102, 120.

In this embodiment, when thermal transfer assembly 400 is mountedbetween casings 102, 120 as described above, radially inner surface 407of body 402 may contact (or is closely positioned) to driver assembly300 (particularly coils 304). Thus, as will be described in more detailbelow, heat which is generated within coils 304 during operations may betransferred (e.g., conducted, radiated, etc.) to body 402 and thenfurther transferred away from pump 800 via cooling coil 420 as notedabove.

Referring still to FIGS. 2, 7, and 9, diffuser 500 comprises an outerhousing 502, a central hub 506, and a plurality of diffuser vanes 508(or more simply “vanes 508”) extending between central hub 506 and outerhousing 502.

In this embodiment, outer housing 502 is a cylindrical member thatincludes a first or upstream end 502 a, a second or downstream end 502 bopposite upstream end 502 a. In addition, outer housing 502 includes aradially outer cylindrical surface 504 and a radially inner cylindricalsurface 503 both extending axially between ends 502 a, 502 b. In otherembodiments, outer housing 502 (or a portion thereof), may benon-cylindrical in shape.

Referring still to FIGS. 2, 7, and 9, central hub 506 is a solid member(non-hollow) disposed within outer housing 502 along axis 805 andincludes a first or upstream end 506 a, a second or downstream end 506 bopposite upstream end 506 a. Upstream end 506 a extends axially pastupstream end 502 a of outer housing 502, and downstream end 506 b isdisposed at downstream end 502 b of outer housing 502. In addition,central hub 506 includes a first or upstream section 507 extendingaxially from upstream end 506 a, and a second or downstream section 509extending axially from upstream section 507 to downstream end 506 b.Upstream section 507 is generally cylindrical in shape, while downstreamsection 509 is generally conical in shape. Thus, of diffuser 500 mayinclude a varying cross-section between ends 502 a, 502 b. In thisembodiment, the circumference and diameter of central hub 506 isgenerally constant within upstream section 507, and generally decreaseswhen moving axially within downstream section 509 from upstream section507 to downstream end 506 b. In addition, in this embodiment downstreamend 506 b includes a rounded or hemispherical surface 510. Without beinglimited to this or any other theory, the hemispherical surface 510 mayreduce turbulence for the fluid flowing within outer housing 502 and thegenerally conical shape of downstream section 509 of central hub 506 mayprogressively increase the flow area within outer housing 502 for fluidsflowing from upstream end 502 a toward downstream end 502 b. It shouldbe appreciated that other shapes and profiles are contemplated forcentral hub 506. For example, in some embodiments, central hub 506 mayinclude non-linear cross-section changes (e.g., a parabolic).

Referring specifically now to FIG. 7, vanes 508 extend generallyradially outward from central hub 506 to radially inner surface 503 ofouter housing 502. Each vane 508 includes a first or upstream end 508 aand a second or downstream end 508 b opposite upstream end 508 a.Upstream end 508 a is proximate upstream end 502 a of outer housing 502and downstream end 508 b is proximate downstream end 502 b of housing502. In some embodiments, vanes 508 are circumferentially spaced (e.g.,uniformly circumferentially spaced) about axis 805. In this embodiment,there are total four vanes 508, that are circumferentially spacedapproximately 90° from one another about axis 805; however, othernumbers and spacing are contemplated for vanes 508 in other embodiments.In addition, each of the vanes 508 of this embodiment are configured togenerally convert a twisting or helical flow pattern for a fluid (e.g.,such as a fluid that has flowed across impeller 202 previouslydescribed) into a generally axial or laminar flow pattern. That is,vanes 508 are configured to straighten the fluid flowing from impeller202. Thus, in this embodiment, each vane 508 extends generally helicallyat upstream end 508 a, but then progressively transitions to a generallyaxial orientation at downstream end 508 b. In one embodiment, theupstream end 508 a vanes 508 may generally correspond (e.g., having asimilar or equal helical angle, pitch, etc.) to the helical direction orshape of vanes 208 of impeller 202 (see e.g., FIGS. 2 and 5) such thatfluid flowing past impeller 200 is efficiently captured by diffuser 500,during operations.

Referring still to FIG. 7, in this embodiment, vanes 508 extendgenerally helically along portions of central hub 506 proximate toupstream end 508 a and couple with radially inner surface 503 of housing502. In addition, in this embodiment the axial thickness of each vane508 generally decreases when moving from central hub 506 toward radiallyinner surface 503. However, again, in other embodiments, the axialthickness of vanes 508 may be generally may be constant between centralhub 506 and radially inner surface 503. Further, while not specificallyshown it should be appreciated that the axial thickness of each vane 508may vary (e.g., increase and/or decrease) or may remain generallyconstant between its corresponding upstream and downstream ends 508 a,508 b, respectively. Still further, in some embodiments localcross-sectional variations may be included along vanes 508 to optimizeflow characteristics through diffuser 500 during operations. Also, insubstantially the same manner as was previously described for the vanes208 of impeller 200, in some embodiments the general helical shape ofvanes 508 of diffuser 500 (e.g., for the portion of vanes 508 proximateupstream end 508 a) may vary (e.g., in helical pitch) along the axialdirection and/or the radial direction with respect to axis 805.

In this embodiment outer housing 502, central hub 506, and vanes 508 areall monolithically formed as a single piece or member (i.e., diffuser500). Thus, in some embodiments, outer housing 502, central hub 506, andvanes 508 may comprise the same material(s) (e.g., fiberglass). Duringoperations, fluid is flowed over the diffuser 500 (including outerhousing 502, central hub 506, and vanes 508) to transition the flowpattern of the fluid from helical or twisting to laminar (or morelaminar). Because vanes 508 are monolithically formed with outer housing502 and central hub 506 as previously described, fluids flowing throughdiffuser 500 (e.g., between ends 502 a, 502 b of outer housing 502) areprevented from flowing between outer housing 502 and vanes 508 andbetween vanes 508 and central hub 506. Accordingly, the fluid is forcedto flow over vanes 508 as it flows axially between ends 502 a, 502 b ofhousing 502.

Referring again to FIG. 2, diffuser 500 is inserted within downstreamsection 124 b of throughbore 124 in discharge casing 120 duringoperations. In particular, diffuser 500 is inserted axially intodownstream section 124 b of throughbore 124 from downstream end 120 b ofcasing 120 until upstream end 502 a of outer housing 502 engages withdownstream facing annular shoulder 139, and upstream end 506 a ofcentral hub 506 approaches downstream end 206 b of central hub 206 alongaxis 805. Thereafter a retaining ring 520 is inserted within throughbore124 (particularly downstream section 124 b) and is radially expandedinto annular recess 138. Thus, during operations, diffuser 500 isprevented from axially translating out downstream section 124 b ofthroughbore 124 by engaging with retaining ring 520.

Referring now to FIGS. 1 and 11, during operations, turbine pump 800 ismounted within a fluid line (e.g., fluid line 920). In particular, inthis embodiment, pump 800 is mounted within pump system 1000 betweenupstream section 920 a and downstream section 920 b of fluid line 920 sothat axes 805, 925 are generally aligned with one another as previouslydescribed. More specifically, as best shown in FIG. 11, in thisembodiment, upstream connector 106 on suction casing 102 is engaged witha corresponding connector 910 a on upstream section 920 a and downstreamconnector 126 on discharge casing 120 is engaged with a correspondingconnector 910 b on downstream section 920 b. Connectors 910 a, 910 binclude a plurality of bolt holes 912 that are aligned with theplurality of bolt holes 116, 142 on casings 102, 120, respectively. As aresult, during operations, fasteners (e.g., bolts) (not shown) areinserted through aligned pairs of the bolt holes 912 in connector 910 aand bolt holes 116 in connector 102 and through aligned pairs of boltholes 912 in connector 910 b and bolt holes 142 in downstream connector126. In addition, while note shown, it should be appreciated that asuitable sealing member (or members) (e.g., a gasket, O-ring, etc.) maybe disposed between the engaged connectors 910 a, 116 and 910 b, 126 soas to prevent fluids flowing within fluid line 920 and pump 800 fromleaking during operations.

Upstream section 920 a and downstream section 920 b of fluid line 920each include a corresponding flow bore 922 a and 922 b, respectively.When pump 800 is mounted between sections 920 a, 920 b as describedabove, flow bore 922 a of upstream section 920 a is in fluidcommunication with flow bore 922 b of downstream section 920 b throughthe throughbore 104 of suction casing 102, the outer housings 204, 502of impeller 202 and diffuser 500, respectively, (as well as the centralapertures 211, 221 of wear rings 210, 220 on either side of impeller202), and the throughbore 124 of discharge casing 120. In addition, asshown in FIG. 10, when pump 800 is mounted between sections 920 a, 920 bas described above, upstream section 104 a of throughbore 104 (see e.g.,FIG. 3), central apertures 211, 221 of wear rings 210 a, 210 b, 220 a,220 b, respectively, projection 136 within throughbore 124, and radiallyinner surfaces 203, 503 of outer housings 204, 502 of impeller 202 anddiffuser 500, respectively, are all generally flush with the radiallyinner surface defining the flow bore 922 a within upstream section 920a. Without being limited to this or any other theory, fluids mayexperience less disturbance due to the flush orientation of fluid flowbore 922 a and the above noted surfaces within pump 800 duringoperations, so that pump 800 may operate an a higher level of efficiencyduring operations.

Referring still to FIGS. 1 and 10, during operations, driver assembly300 induces a varying magnetic field to thereby rotate impeller 202about axis 805 within casing assembly 100 as previously described above.As impeller 202 rotates about axis 805, turbine pump 800 produces fluidflow through fluid line 920 from upstream section 920 a to downstreamsection 920 b in flow direction 950. During these operations, diffuser500 remains generally stationary, and serves to transition the fluidflowing from impeller from a helical or twisting flow to a more laminarflow downstream of turbine pump 800 as previously described above.

Additionally, during the above described operations, thermal transferassembly 400 cools driver assembly 300, which may be prone to heating bythe electrical current flowing therein, As previously described above,thermal transfer assembly 400 may transfer heat away from driverassembly 300 via body 402 as well as with cooling coil 420, Forinstance, referring now to FIGS. 12, in some embodiments cooling coil420 may receive a recycle stream of fluid from fluid line 920 and inparticular from downstream section 920 b during operations. in thisembodiment, a relatively small amount of the fluid flowing through fluidline 920 is diverted from downstream section 920 b and is supplied tocooling coil 420 via a conduit 923 (e.g., tubing). After flowing throughcooling coil 420, the fluid is then recycled back to fluid line 920 viaa conduit 924 (e.g., tubing 924), such as at a position upstream of pump800 (e.g., within upstream section 920 a as shown). After being emittedfrom cooling coil 420, the fluid may be at an elevated temperature, andthus, may be routed through a suitable heat exchanger prior to flowingback into fluid line 920 (e.g., upstream section 920 a) as previouslydescribed above.

Referring to FIG. 13, in other embodiments of turbine pump 800, aseparate fluid (that is, a fluid that is not the fluid flowing throughfluid line 920) may be flowed through cooling coil 420 to facilitateheat transfer operations. in particular, in this embodiment coolingfluid (e.g., air, water, ethyl glycol, oil, or two-phase evaporativefluids such as R134a, etc.) is supplied to cooling coil 420 from aself-contained cooling unit 1250 via a conduit 1252 (e.g., tubing). Onceemitted from the cooling coil 420, the cooling fluid may be recycledback to cooling unit 1250 via a conduit 1254 (e.g., tubing) (which mayinclude one or more heat exchangers, pumps, etc.).

In some embodiments, components of turbine pump 800 (e.g., impeller 202,diffuser 500, etc.) may be manufactured out of non-metallic materials(e.g., fiberglass, carbon fiber, aramid fiber) such that the pump 800may be more effectively utilized to pump corrosive fluids (e.g., such assalt water). Accordingly, an example manufacturing process is describedbelow for manufacturing some or all of the components of pump 800. Themanufacturing process described herein is employs a resin transfermolding (RTM) process. During RTM molding, reinforcing fibers, such asfiberglass, are oriented prior to the injection of resin into the mold,thereby increasing the strength of the molded component in the directionof fiber orientation. However, it should be appreciated that themanufacturing process described herein can be applied to other types ofmolding processes, such as, for example, compression molding. Duringcompression molding, the orientation of the reinforcing fibers isgenerally less controlled or uncontrolled, thus causing thecompression-molded component to have a greater thickness than a likeRIM-molded component having a given strength.

Generally speaking, when manufacturing the components (or some of thecomponents) of pump 800, a mold core having a shape that is the inverseof the molded component is disposed inside a mold cavity. In someembodiments, the mold core may comprise a wax. For example, the waxcomprising the core may comprise a “Blue Blend” machinable wax, a waxcommercially available from “Machinable Wax.com”, Lake Ann, Mich. Insome embodiments, the “Blue Blend” wax has a Specific density ofapproximately 0.035 pounds/cubic inch, a hardness of 50-55 (Shore I)scale), a flash point of 575° F., a softening point of 226° F., a dropmelting point of 227° F., and a 5% volumetric shrinkage rate. Inaddition, in some embodiments, the wax comprising the mold core iscarveable.

Referring to FIG. 14, a wax structure 60 is illustrated which may beused to produce impeller 202 (see e.g., FIG. 5), yet a similar proceduremay be used for diffuser 500 (see e.g., FIG. 7) as well as othercomponents of pump 800. More particularly, wax structure 60 has a shapesuitable to provide a mold core 62 that is disposed inside a mold cavityso as to facilitate fabrication of a RTM-fabricated impeller 202. Thus,the size of mold core 62 may be defined by the geometry of the desiredwax structure 60. In particular, mold core 62 defines an inversestructure of impeller 202, such that solid regions of mold core 62defines open regions or air pockets along impeller 202 that arematerial-free, while open regions or air pockets defined by mold core 62defines solid structures along impeller 202. In order to preventcracking as wax structure 60 cools, mold dies that define the shape ofwax structure 60 may be made of silicon rubber. Silicon rubber minimizesthe dissipation of heat as wax structure 60 hardens during fabricationof wax structure 60. Additionally, heat lamps may be selectively usedduring the fabrication of wax structure 60 to prevent local hardening ofthe wax, for example at the open end of the mold which is exposed toambient air temperatures. This local heating technique allows the wax tocool slowly, along a direction from the closed portion (e.g., the base)of mold core 62 towards the open end of mold core 62, thereby minimizingthe possibility of forming cracks in the wax during cooling. Multi-axiscomputer numerical control (CNC) machines can mill or otherwise machinecutouts 64 in wax structure 60 that are in the shape of impeller vanes208.

During operations, reinforcing fibers (not shown), such as fiberglassfibers, are oriented along a desired direction, placed along the outerand inner surfaces of mold core 62, and are also inserted along cutouts64. As best shown in FIGS. 15 and 16, the fiberglass-carrying core 62 isplaced into a mold cavity 72 that is defined between a pair of mold dies74, and a resin is injected into the mold cavity 72 to form impeller202. Once the resin hardens, mold dies 74 may be separated to revealimpeller 202.

The injected resin may be any suitable resin, such as, for example anon-corrosive resin (e.g., as a vinyl-ester or epoxy). In someembodiments, the injected and cured resin has a melting point of greaterthan 350° F., and greater than that of wax mold core 62, such that waxmold core 62 may be melted away without damaging impeller 202. In someembodiments, the resin may heated to facilitate the curing thereof, andthus it may be possible to select a mold curing temperature thatconcurrently cures and removes mold core 62. For example, 267° F. mayprovide a suitable curing temperature in some embodiments which may meltaway a wax mold core 62 made of Blue Blend wax (e.g., above 227° F.)without melting the cured resin at 350° F.

Any residual wax which may remain on impeller 202 after wax core 62 ismelted, may be flushed out of turbine pump 800 during operations,Without being limited to this or any other theory, the residual wax maybe soft enough such that it may pass through turbine pump 800 and fluidline 920 during normal operations.

It should be appreciated that both the molded impeller 202 and diffuser500 are homogeneous one piece solid components when produced by themethods described herein above. More particularly the elements of eachcomponent are fabricated as a single integral structure, free of jointsin the form of glue, non-molded resin, bolts, fasteners, or otherdiscrete connections. For example, impeller vanes 208 are integrallyconnected to both outer housing 204 and central hub 206. Likewise,diffuser vanes 508 are integrally connected to outer surface 502 andcentral hub 506.

In the manner described, embodiments disclosed herein include turbinepumps with integrated motor or drive units (e.g., pump 800), which mayallow the pumps to be installed and supported within segments of a fluidline (e.g., fluid line 920). As a result, a separate support base orfoundation for the motor or drive unit of the pump may be omitted. Inaddition, some embodiments of the turbine pumps disclosed herein areconstructed (wholly or partially) of non-metallic materials, such thatthey may be used to pump corrosive fluids (e.g., salt water).

While some embodiments of the pump 800 described above have included amagnet assembly 230 that is separately secured to impeller 202, itshould be appreciated that in other embodiments, magnet assembly 230 (orportions thereof) are integrated or monolithically formed with impeller202. For instance, in some embodiments, magnets 240 of magnet assembly230 may be molded onto and/or within outer housing 204 of impeller 202during an embodiment of the above described manufacturing process. Thatis, the magnets 240 may be placed within the mold cavity along with core62 (see FIGS. 15 and 16) so that the resulting impeller 202 may havemagnets embedded therein. In addition, some of the embodiments of pump800 may supplement or replace cooling coils 420, with other thermaltransfer devices. For instance, in these embodiments, thermal transferassembly 400 may include a so-called cooling jacket to channel or flow avolume of cooling fluid about body 402. For example in some embodiments,body 402 may define or include a channel or annulus that may receive aflow of cooling fluid therethrough during operations (e.g., such ascooling fluids discussed above with respect to FIGS. 12 and 13). insonic of these embodiments, the channel or annulus may be subdividedusing fins, baffles, etc. Still further, in some embodiments other heattransfer components or devices may be used within pump either in lieu ofor in addition to those described above fins, blowers, fluid baths,etc.).

Having described various devices and methods, specific embodiments caninclude, but are not limited to:

In a first embodiment, a pump comprises: a casing assembly, wherein thecasing assembly includes a central axis and comprises: an upstreamconnector that is configured to engage with a first connector on a fluidline; and a downstream connector that is configured to engage with asecond connector on the fluid line; an impeller rotatably disposedwithin the casing assembly; and a driver assembly coupled to the casingassembly and annularly disposed about the impeller; wherein the driverassembly is configured to rotate the impeller about the central axis.

A second embodiment can include the pump of the first embodiment,wherein the impeller comprises an outer housing, a central hub, and aplurality of vanes engaged with and extending between the central huband the outer housing.

A third embodiment can include the pump of the second embodiment,wherein the outer housing is cylindrical in shape and includes aradially inner cylindrical surface and a radially outer cylindricalsurface, and wherein each of the plurality of vanes is engaged with theradially inner cylindrical surface.

A fourth embodiment can include the pump of the third embodiment,wherein the casing assembly comprises a suction casing and a dischargecasing, wherein the suction casing comprises a throughbore that is flushwith the radially inner cylindrical surface of the outer housing of theimpeller.

A fifth embodiment can include the pump of the third or fourthembodiment, wherein the central hub includes a first end and a secondend opposite the first end, wherein the first end of the central hubincludes a hemispherical surface.

A sixth embodiment can include the pump of any one of the third to fifthembodiments, comprising a plurality of magnets coupled to the radiallyouter cylindrical surface of the outer housing of the impeller, whereinthe driver assembly is configured to induce a varying magnetic field torotate the impeller and the plurality of magnets about the central axis.

A seventh embodiment can include the pump of any one of the second tosixth embodiments, wherein the outer housing, the central hub, and theplurality of vanes of the impeller are formed as a monolithic member.

An eighth embodiment can include the pump of the seventh embodiment,wherein the impeller comprises fiberglass.

A ninth embodiment can include the pump of any one of the first toeighth embodiments, further comprising a thermal transfer assemblycomprising: a body annularly disposed about the driver assembly; and acooling coil disposed about the body, wherein the cooling coil comprisesan elongate tube that is configured to receive a flow of cooling fluidtherethrough.

A tenth embodiment can include the pump of the ninth embodiment, whereinthe casing assembly comprises a suction casing and a discharge casing,wherein the body of the thermal transfer assembly is disposed axiallybetween the suction casing and the discharge casing.

In an eleventh embodiment, a system comprises: a first pipe section; asecond pipe section; and a pump mounted between the first pipe sectionand the second pipe section, wherein the pump comprises: a casingassembly including a central axis; an impeller rotatably disposed withinthe casing assembly; and a driver assembly coupled to the casingassembly and annularly disposed about the impeller; wherein the driverassembly is configured to rotate the impeller about the central axis topump fluid from the first pipe section to the second pipe section.

A twelfth embodiment can include the system of the eleventh embodiment,wherein the impeller comprises: a cylindrical outer housing; a centralhub disposed within the outer housing; and a plurality of impeller vanesengaged with and extending between the central hub and the outerhousing.

A thirteenth embodiment can include the system of the twelfthembodiment, further comprising: a diffuser disposed within the casingassembly, axially adjacent the impeller, wherein the diffuser isconfigured to straighten a flow of fluid flowing from the impeller; andwherein the diffuser comprises: a cylindrical outer housing; a centralhub disposed within the outer housing of the diffuser; and a pluralityof diffuser vanes engaged with and extending between the central hub ofthe diffuser and the outer housing of the diffuser.

A fourteenth embodiment can include the system of any one of theeleventh to thirteenth embodiments, further comprising a thermaltransfer assembly comprising: a body mounted to the casing assembly anddisposed annularly about the driver assembly; and a cooling coildisposed about the body, wherein the cooling coil comprises an elongatetube that is configured to receive a flow of cooling fluid therethrough.

A fifteenth embodiment can include the system of the fourteenthembodiment, wherein the cooling coil is fluidly coupled to the firstpipe section and the second pipe section.

In a sixteenth embodiment, a method of pumping a fluid through a fluidline comprises: mounting a pump between a pair of pipe sections of thefluid line, wherein the pump comprises: a casing assembly including acentral axis; an impeller rotatably disposed within the casing assembly;and a driver assembly coupled to the casing assembly and annularlydisposed about the impeller; rotating the impeller about the centralaxis with the driver assembly; and flowing a fluid through the pair ofpipe sections and the pump while rotating the impeller.

A seventeenth embodiment can include the method of the sixteenthembodiment, further comprising: straightening a flow of the fluid with adiffuser disposed axially adjacent the impeller.

An eighteenth embodiment can include the method of the sixteenth orseventeenth embodiment, wherein rotating the impeller comprises:inducing a varying magnetic field with the driver assembly; andattracting a plurality of magnets with the varying magnetic field.

A nineteenth embodiment can include the method of any one of thesixteenth to eighteenth embodiments, further comprising: flowing acooling fluid through a coil that is wrapped about a body of a thermaltransfer assembly, wherein the body is mounted to the casing assemblyand is disposed annularly about the driver assembly.

A twentieth embodiment can include the method of the nineteenthembodiment, wherein flowing the cooling fluid through the coilcomprises: flowing a stream of fluid from a downstream section of thepair of pipe sections to the coil; and flowing the stream of fluidthrough the coil after; and flowing the stream of fluid from the coil toan upstream section of the pair of pipe section after flowing the streamthrough the coil.

While exemplary embodiments have been shown and described, modificationsthereof can be made by one skilled in the art without departing from thescope or teachings herein. The embodiments described herein areexemplary only and are not limiting. Many variations and modificationsof the systems, apparatus, and processes described herein are possibleand are within the scope of the disclosure. Accordingly, the scope ofprotection is not limited to the embodiments described herein, but isonly limited by the claims that follow, the scope of which shall includeall equivalents of the subject matter of the claims. Unless expresslystated otherwise, the steps in a method claim may be performed in anyorder. The recitation of identifiers such as (a), (b), (c) or (1), (2),(3) before steps in a method claim are not intended to and do notspecify a particular order to the steps, but rather are used to simplifysubsequent reference to such steps.

What is claimed is:
 1. A pump comprising: a casing assembly, wherein thecasing assembly includes a central axis and comprises: an upstreamconnector that is configured to engage with a first connector on a fluidline; and a downstream connector that is configured to engage with asecond connector on the fluid line; an impeller rotatably disposedwithin the casing assembly; and a driver assembly coupled to the casingassembly and annularly disposed about the impeller; wherein the driverassembly is configured to rotate the impeller about the central axis. 2.The pump of claim 1, wherein the impeller comprises an outer housing, acentral hub, and a plurality of vanes engaged with and extending betweenthe central hub and the outer housing.
 3. The pump of claim 2, whereinthe outer housing, the central hub, and the plurality of vanes of theimpeller are formed as a monolithic member.
 4. The pump of claim 3,wherein the impeller comprises fiberglass.
 5. The pump of claim 2,wherein the outer housing is cylindrical in shape and includes aradially inner cylindrical surface and a radially outer cylindricalsurface, and wherein each of the plurality of vanes is engaged with theradially inner cylindrical surface.
 6. The pump of claim 5, wherein thecasing assembly comprises a suction casing and a discharge casing,wherein the suction casing comprises a throughhore that is flush withthe radially inner cylindrical surface of the outer housing of theimpeller.
 7. The pump of claim 5, wherein the central hub includes afirst end and a second end opposite the first end, wherein the first endof the central hub includes a hemispherical surface.
 8. The pump ofclaim 5, comprising a plurality of magnets coupled to the radially outercylindrical surface of the outer housing of the impeller, wherein thedriver assembly is configured to induce a varying magnetic field torotate the impeller and the plurality of magnets about the central axis.9. The pump of claim 1, further comprising a thermal transfer assemblycomprising: a body annularly disposed about the driver assembly; and acooling coil disposed about the body, wherein the cooling coil comprisesan elongate tube that is configured to receive a flow of cooling fluidtherethrough.
 10. The pump of claim 9, wherein the casing assemblycomprises a suction casing and a discharge casing, wherein the body ofthe thermal transfer assembly is disposed axially between the suctioncasing and the discharge casing.
 11. A system, comprising: a first pipesection; a second pipe section; and a pump mounted between the firstpipe section and the second pipe section, wherein the pump comprises: acasing assembly including a central axis; an impeller rotatably disposedwithin the casing assembly; and a driver assembly coupled to the casingassembly and annularly disposed about the impeller; wherein the driverassembly is configured to rotate the impeller about the central axis topump fluid from the first pipe section to the second pipe section. 12.The system of claim 11, wherein the impeller comprises: a cylindricalouter housing; a central hub disposed within the outer housing; and aplurality of impeller vanes engaged with and extending between thecentral hub and the outer housing.
 13. The system of claim 12, furthercomprising: a diffuser disposed within the casing assembly, axiallyadjacent the impeller, wherein the diffuser is configured to straightena flow of fluid flowing from the impeller; and wherein the diffusercomprises: a cylindrical outer housing; a central hub disposed withinthe outer housing of the diffuser; and a plurality of diffuser vanesengaged with and extending between the central hub of the diffuser andthe outer housing of the diffuser.
 14. The system of claim 11, furthercomprising a thermal transfer assembly comprising: a body mounted to thecasing assembly and disposed annularly about the driver assembly; and acooling coil disposed about the body, wherein the cooling coil comprisesan elongate tube that is configured to receive a flow of cooling fluidtherethrough.
 15. The system of claim 14, wherein the cooling coil isfluidly coupled to the first pipe section and the second pipe section.16. A method of pumping a fluid through a fluid line, the methodcomprising: mounting a pump between a pair of pipe sections of the fluidline, wherein the pump comprises: a casing assembly including a centralaxis; an impeller rotatably disposed within the casing assembly; and adriver assembly coupled to the casing assembly and annularly disposedabout the impeller; rotating the impeller about the central axis withthe driver assembly; and flowing a fluid through the pair of pipesections and the pump while rotating the impeller
 17. The method ofclaim 16, further comprising: straightening a flow of the fluid with adiffuser disposed axially adjacent the impeller
 18. The method of claim16, wherein rotating the impeller comprises: inducing a varying magneticfield with the driver assembly; and attracting a plurality of magnetswith the varying magnetic field.
 19. The method of claim 16, furthercomprising: flowing a cooling fluid through a coil that is wrapped abouta body of a thermal transfer assembly, wherein the body is mounted tothe casing assembly and is disposed annularly about the driver assembly.20. The method of claim 19, wherein flowing the cooling fluid throughthe coil comprises: flowing a stream of fluid from a downstream sectionof the pair of pipe sections to the coil; and flowing the stream offluid through the coil after; and flowing the stream of fluid from thecoil to an upstream section of the pair of pipe section after flowingthe stream through the coil.